Pavement cutting machine with selected drive system

ABSTRACT

A pavement cutting machine for cutting bumps or grooves. A tractor has a hitch with a cutter trailer and a tank trailer. The tank picks up the sludge from the cutter, filters it and recirculates the filtered water to the cutter. One or more hydraulic cylinders for the cutter or cutters act against a frame member which supports the tank whereby the weight of the tank snubs the cutter or cutters. The tractor has an engine for driving the traction wheels of the vehicle at high speed when moving from one location to another. The tractor has an alternative hydraulic drive operated by the engine when the engine is disconnected from the traction wheels, the hydraulic drive having a low speed transmission to the traction wheels.

Hatcher et al.

[ PAVEMENT CUTTING MACHINE WITH SELECTED DRIVE SYSTEM [76} Inventors:Cecil W. Hatcher; Gene Warner, both of PO. Box 1263, El Monte, Calif.91734 [22] Filed: Aug. 18, 1972 [21] Appl. No.: 281,952

Related U.S. Application Data [62] Division of Ser. No. 119,476, March1, 1971, Pat.

[52] U.S. Cl. 299/39, 173/24, 180/53 CD [51] Int. Cl. E0lc 23/09 [58]Field of Search 299/39; 180/53 CD; 173/24 [56] References Cited UNITEDSTATES PATENTS 2,783,556 3/1957 Burns et al. 180/53 CD 1 Dec. 18, 1973Att0meyWlliam E. Beatty [57] ABSTRACT A pavement cutting machine forcutting bumps or grooves. A tractor has a hitch with a cutter trailerand a tank trailer. The tank picks up the sludge from the cutter,filters it and recirculates the filtered water to the cutter. One ormore hydraulic cylinders for the cutter or cutters act against a framemember which supports the tank whereby the weight of the tank snubs thecutter or cutters. The tractor has an engine for driving the tractionwheels of the vehicle at high speed when moving from one location toanother. The tractor has an alternative hydraulic drive operated by theengine when the engine is disconnected from the traction wheels, thehydraulic drive having a low speed transmission to the traction wheels.

8 Claims, 29 Drawing Figures PATENTEDHEB 1 8 ms SNEEF 03 0F 12 Ma k fiWHENTED DEC 1 8 I973 SHEET UBUF 12 MENTEDUEB 18 I975 SHEET 07 0F 12 W SmQ Q bi PMENTEUUEC 18 I975 SHEET IOUF 12 mum .WWRG @I mw Rig PAVEMENTCUTTING MACHINE WITH SELECTED DRIVE SYSTEM BACKGROUND OF THEINVENTION 1. Field of the Invention The invention relates to a pavementleveling or grooving machine having a vehicle having a pavement cutterwherein a tractor pulls the cutter vehicle and a water tankerrecirculating water to cool the cutter disks.

2. Description of the Prior Art As is well known in the art, there arevarious machines used for grooving or leveling road surfaces. However,each of the known devices have limitations, and problems associated withthem. One problem is the transporting of the machines from one operationsite to another and, after reaching the site, being able to operateunder ideal conditions to properly complete the work required. Anotherarea where the present machines are lacking is the capability of keepingthe required depth of the grooves as the cutter assembly, or assemblies,make their pass over a road bed having an uneven surface. It is alsonecessary to have a machine that is not only capable of grooving theroad surface but, in addition, serving a dual purpose as a levelingapparatus. se'fiesofdiambnd blades or disks are generally used for theleveling and grinding of the grooves, these blades being very expensiveand, if not properly prot'ected,v each can be damaged and becomeineffective .si rinai wqt sinsgnqrati n-"Dama e-i likell 9 occur if thecutter blades meet an obstruction when (I 9..P IPIHQE LEJII t l w,Speed. b a P erf direc l t h a tqr. wa la -suMMAsxQ TH INVENTJQN.

The invention comprises a dual tandem apparatus for leveling or groovingroads and highway surfaces, whereby cars and the like will besubstantially protected from skidding, especially in wet weather. Thedual tandem apparatus comprises a tractor having a cab section fortransporting the entire machine down the highway to a work location, afirst trailer section positioned intermediate to the tractor and asecond trailer section. The first trailer section is operably connectedto the tractor as a pavement leveling and grooving machine, an thesecond end trailer is a tanker for supplying a liquid coolant, such aswater, to the grooving and leveling apparatus. The tractor section isadapted with the equipment and controlling apparatus to operate themovement of the entire vehicle while traveling down the highway to awork location by use of a direct drive to its rear-wheel drive atmoderately high speeds with its total complement of trailers. If theDiesel? engine in the tractor were to operate at low gear and drive theequipment at a slow speed, the engines powerful-direct drive woulddamage parts related to the grooving apparatus, if theparts met anobstruction.

The vehicle will travel at high speed by a drive from an engine througha four-speed transmission, as usual. For lowspeed operation of thevehicle, a clutch is operated to disconnect the engine which continuesto run and operate two pumps, each through a separate power takeoff. Onepump provides fluid pressure for hydraulic cylinders to raise or lowerthe cutter and the other pump provides fluid pressure for a fluid motorwhich drives the traction wheels through the main four-speedtransmission. The cutter is driven by a seoarate engine.

BRIEF DESCRIPTION OF THE DRAWINGS Referring more particularly to theaccompanying drawings, which are for illustrative purposes only:

FIG. 1 is a side-elevational view of the invention showing a tractorpulling a cutter trailer and a water tank trailer.

FIG. 2 is a top plan view of FIG. 1.

FIG. 3 is a sectional view taken on line 3-3 of FIG.

FIG. 4 is a sectional view taken on line 44 of FIG. 3.

FIG. 5 is a fragmentary perspective view of a filter unit as seen inFIG. 3.

FIG. 6 is a schematic cross-sectional view of the tank trailer and thevacuum system.

FIG. 7 is an enlarged side view of the grooving trailer with portionsbroken away for clearer illustration thereof.

FIG. 8 is a top plan view of FIG. 7 on line 8-8 thereof.

FIG. 9 is a cross-sectional view taken on line 9-9 of FIG. 8.

FIG. 10 is a cross-sectional view taken on line 10-10 of FIG. 9.

FIG. 11 is a cross-sectional view taken substantially on line 11-11 ofFIG. 9 thereof.

FIG. 12 is an enlarged sectional view taken on line 12-12 of FIG. 11.

FIG. 13 is an enlarged sectional view taken on line 13-13 of FIG. 12showing the cutter blades cutting grooves in a road surface.

FIG. 14 is an enlarged sectional view taken substantially on line 14-14of FIG. 11.

FIG. 15 is a sectional view taken substantially on line 15-15 of FIG.14.

FIG. 16 is an enlarged plan view of a portion of the grooving trailerpositioned adjacent a curbing of a road surface.

FIG. 17 is a sectional view taken substantially on line 17-17 of FIG. 11thereof.

FIG. 18 is a view illustrating the depth control wheel assembly foradjusting the depth of cut of the blades of the cutting assembly forcutting grooves.

FIG.19 is an exploded perspective view of a supporting bracket of awater nozzle spray unit.

FIG. 20 is a partial perspective view of the grooving trailer assembly.

FIG. 21 is a sectional view illustrating the cutting assembliessupported in a somewhat universal mounting and positioned for cutting anirregular road surface.

FIG. 22 is a partial top plan view of the cutting assemblies with theirinner ends adjacent each other.

FIG. 23 is a sectional view of a modified form of depth control for thecutting assembly adapted for cutting bumps.

FIG. 24 is a flow diagram of the hydraulic system for controlling theover-all operation of the leveling or grooving machine.

FIG. 25 is a schematic view of the transmission and power take-off shownin FIG. 24.

FIG. 26 is an enlarged fragmentary sectional view on line 26-26 of FIG.23.

FIGS. 27, 28 and 29 are schematic views of modifications of the frameand floating beam support for the cutter or cutters.

DESCRIPTION OF THEPREFERRED V EMBODIMENT Referring more particularly tothe drawings, there is shown in FIG. 1 a tractor-trailer vehicle,generally indicated at 10, comprising a tractor, indicated generally at12, which is provided with a typical cab 14 and a Diesel or similarengine 16 mounted at the front end of the tractor frame 18. The frame 18is provided with a swivel bed or hitch 20 for an operable connectionbetween the tractor and tandem trailer. Tractor is movably supported byaset of front wheels 22 for steering the vehicle and a back set of drivewheels 24 as generally found in such a vehicle H However, there isincluded means for disengaging the engine power from the rear drive ortraction wheels 24 to engage a hydraulic drive system when required. Amore detailed description of said means will be described hereinafter.

There is operably connected to the swivel bed or hitch of the tractor 12a first tandem trailer unit 26 and a second tandem trailer unit 28 whichis operably gonrrected to said first trailer unit 26 by a swivel bedprhitch 29, supported on the rear of said first trailer unit. The firsttrailer unit 26 includes a leveling or grooving machine having a rotarycutter assembly 45, having a hitch 55 with the frame structure 30 whichin turn has a hitch 20 with the tractor 12.

The trailer unit 26 comprises a carriage or frame structure 30 having asomewhat Z-shaped configuration which includes a horizontal boxframework 32 having a mating member 33 for the swivel bed 20 and aplatform 34, as seen in FIG. 2. Positioned rearwardly of said platform34 and attached to frame 32 are a pair of parallel vertical beams 36, 36spaced apart suffi ciently to receive a transverse support bar 37, asseen in FIGS. 11 and 20. The beams 36, 36 are securedto the box frame 32intermediate their ends. Rearwardly disposed from said beams 36, 36 is asecond pair of matching beams 38, 38, said beams 36 and 38 beinginterconnected by overhead horizontal girder member 39, and beams 36'and 38 being similarly interconnected by an overhead horizontal girdermember 39. The girders 39, 39 have suitable transverse supports shown asI-beams 41 and 43, see FIGS. 2 and 7, welded at their ends into thegirders 39, 39'. Attached to the lower portion of the rear verticalbeams 38, 38 is a set of parallel frame members 40, a (FIGS. 8 and 20)having a platform to support the second swivel bed or hitch member 29(FIG. 1). To carry the rear portion of the frame structure 30, there isprovided a set of tandem wheels 42 positioned directly under the swivelbed member 29 whereby the front end of the second trailer 28 is operablyconnected thereto. The trailer 28 has rear wheels 165.

Referring more particularly now to FIGS. 7, 8, 9 and 11, in which a moredetailed construction of the frame structure 30 is shown, there isprovided a rotary cutter assembly, generally indicated at 45, operablymounted within the frame structure 30 of the carriage, said cutterassembly 45 comprising an independent drive engine 46 for operating apair of rotary cutter units, indicated generally at 48 and 50,respectively. There is also provided means for supporting one of saidcutting units in advance of the other, with the inner ends of saidcutter units in substantial alignment. The supporting means comprises aU-shaped frame structure 52, as seen in FIGS. 8, 11 and 20, hingedlyconnected, as indicated at 53, at its forward open end to a header 54,said header 54 having a hitch 55 ,which includes an upper ball member55a secured to the header 54 and a cooperating lower mating socketmember 55b horizontally projecting from and secured to the transversesupport bar 37. Oppositely and rearwardly disposed from the header '54is th e bight portion 57 of the U-shaped frame 52, said bight 57 being arear transverse member having mounted thereon a slide 56 in the form ofa cylindrical pin which is rotatably received in and guided for verticaland pivotal movement by vertical spaced angle irons providing slot means58 carried by bracket 40' depending from frame members 40, 40 a, seeFIG. 20. The slot means 58 prevents lateral movement of said frame 52with respect to the frame structure 30, while permitting rockingmovement about a horizontal axis.

The beams 36, 36', see FIG. 20, have an angle bracket 49, 49,respectively, extending over the header 54 at opposite sides of itslongitudinal axis to limit pivotal movement of header 54 about thataxis, particularly when acted on by hydraulic cylinders 96 and 97,described later.

Due to the ball and socket hitch 55 at one end of the frame 52 and theslide 56 rotatably received in slot 58, the frame and cutter assembly 45together are capable of being angularly adjustable about a horizontalaxis aa, seen in FIG. 11, said hitch and said slide permitting saidcutter units to be readily adapted to inclined surface, when required.

An independent engine 46 is used to impart the rotary movement necessaryto operate the cutter units 48 and 50, said engine being mounted to thefloating U- shaped frame 52 adjacent the bight portion 57 of the U bytransverse channel members 59 secured at their ends to the side members60, 60 of the frame 52. The power output shaft 61 of the engine 46 isproviied with a plurality of pulleys 62 operably connected to pulleys 63by belt 64, said pulleys 63 being securely disposed adjacent one end ofa transverse shaft 65 which is rotatably supported in bearings 66.Disposed on the outer free ends of the shaft 65 are a plurality ofadditional pulleys 67 and 68, respectively. Said pulleys 67 and 68 areoperably interconnected to cutter units 48 and 50 by drive belts 69 and70, respectively. As shown in FIG. 7, belts 69 loop over the upperpulleys 67 to a set of lower pulleys 71 which are attached to a rotaryshaft 72 of the cutter unit 48 adjacent one side of the frame 52. Asshown in FIG. 8, the upper pulleys 68 are oppositely disposed frompulleys 67 on shaft 65 and interconnected to a lower set of pulleys 73secured to a rotary shaft 74 of the cutter unit 50.

As mentioned above, the cutter units 48 and 50 are so arranged that oneassembly is positioned forwardly of the other cutter assembly with theendmost disks 78a, 78'a of their inner ends 75 and 76 spaced apart thesame distance as the spacing between adjacent disks (FIG. 22). Eachcutter unit 4 8 and SI) comprises a plurality of evenly spaced-apartcutter disks 78, 78 having identical diameters and secured on the shafts72 and 74 for rotation therewith. The disks are generally provided withdiamond bits for cutting hard materials, such as cement and concrete.

In FIGS. 15, 20, 21 and 22, the shafts 72 and 74 are shown joumaled attheir outer ends by universal bearings 79 and 80, respectively, saidbearings being suppofid within dual pillow blocks 82 and 83 along therearward section of the side members 60, 60' of the frame 52. However,the inner ends 75 and 76 of cutter units 48 and 50, respectively, havetheir shafts 72 and 74 joumaled in bearings 84 and 85, respectively,supported within dual blocks 86 and 87, spsqt c yt 1 H As shown in FIGS.11 and 20, a pair of parallel floating beams 88 and 90 are providedalong the inner longitudinal length of the frame 52 for supporting theinner ends of each cutter unit. Ech floating beam 88 and 90 isindependently'hinged to the header 54 by brackets 92 and bolts 93,acting as hinge pins, at the forward end thereof. As shown in FIGS. 8,11 and 20, the opposite or rear free end of each beam 88 and 90 ismovably received within the U-shaped brackets 94 and 95, respectively.Said brackets are secured to the rear bight portion 57 of the framemember 52. It should be particularly noted that each beam is capable ofbeing actuated of beams 88, 90 hydraulic cylinders and 102, rep c i x,fo vie in t ear sadp ea floating beam in different or similar verticaldisplacements. The hydraulic cylinders 10] and 102 are hingedlysupported above the adjacent floating beams 88 and 90, respectively, byupside-down- L-shaped brackets 103 and 103a which are fixedly secured tothe rear 57 of the floating frame 52.

FIG. 21 shows an example of how the inner ends of the cutter units 48and 50 can be positioned at a greater elevation than their outer ends'to fit a convex road surface. The inner endg can also be adjusted lowerthan the outer ends id fit a concave road surface. 'r'iifibr,

individually with respect to each other, as well as with respect to thefloating frame 52.

As shown in FIG. the inner support block 86. for

the inner end of shaft 72 is mounted on beam 90,

whereas the block 87 for the inner end of shaft 74 is carried by beam88, with the inner ends of those shafts in overlapping relation as alsoshown in FIG. 22..

c tte s r, groove "set le u pq ss, .a...1?a ns which is substantiallythe same as the spacing between the adjacent disks on each cutterassembly, as indicit ted at 180 which represents the uniform spacing ofkerfs'or grooves in the pavement resulting from the cutting action ofthe innermostdisks of both assemblies. For bump cutting purposes, theinner ends of the cuter may. er apasshsta in.FIQ: 2

As shown in FIGS. 10 and 20, the frame 52 and the rotary cuttingassembly 45 are lifted or lowered by means of a pair of hydrauliccylinders 96 and 97 which are hingedly connected at their lower ends 98and 98' to the rear end of frame 52, and their upper ends 99 and 99' arehingedly connected to the underside of a transverse-extending beam 100which is secured to the rear vertical beams of the frame structure 30.The bightor rear (57 of frame 52 with the cutter assemblies 48 and 50pivots about a horizontal axis passing through the hinge 53 and thehinge pins 93 of the beams 88 and 90. Since the tank trailer 28 isloaded with a dead weight of a large quantity of water, the framestructure and the upper ends of cylinders 96 and 97 are held down fromany vertical movement thereof when the cylinders 96 and 97 areactivated, when the cutter assemblies 48 and 50 are in workingengagement with the pavement. The force of the cylinders 96, 97 buttagainst the over-all weight of the tank which becomes an effectiveopposing force against the lifting effort of the cylinders 96 and 97.Not only can the frame 52 be adjusted vertically, but it can also betilted at an angle through the longitudinal axisq-a (FIG. 11) byadjusting the hydrauliccylind ers 9 6, I i h r is ssqlx s ma t 9.9595 sadjusting the floating beams 88 and 90, the inner ends of said cuttersmay be raised or lowered with respect to their outer ends tosubstantially fit either a convexity or a concavity, as indicated at Ain the pavement 104.

When it is desired to move to a different location and travel atcomparatively high speed with the cutter assemblies 48 and 50 inelevated position, the cylinders 96 and 97 are operated to raise therear end 57 of frame 52, and in so doing, the outer ends of the cutterassemblies are raised, their inner ends and the floating beams 88 andbeing raised by reason of the brackets 94, 95, see FIG. 10. The brackets94, are carried by the frame member 57 and underhang the beams 88 and 90to lift them when the rear end 57 of the frame is lifted. Brackets 94and 95 are open at their tops to permit the upward movement of the beams88 and 90 under working conditions, the brackets 94 and 95 then being ina lowered position free from supporting relation with the beams 88 and90 which are then floated. The operator can adjust the pressure on thecylinders 101 and 102 to adjust the beams 88 and 90 and the inner endsof the cutter assemblies so as to suit working conditions and obtain auniform depth of groove with resulting maximum length of life of thecutter disks.

As shown in FIGS. 1 to 6, 14 and 15, the rotary cutter assembly 45 isprovided with a continuous flow of liquid coolant 106 which consists,generally, of water supplied from cell 162a of tank 44 of the endtrailer 28. This water coolant is pumped by a pumping means 108 which islocated at the front end of the tank 44 and is provided with a pair offlexible conduits, or hoses, 110 and 111 interconnected to separatespray nozzle means, indicated generally at 112 and 112'. IN FIG. 15there can be seen the hoses 110 and 111 attached to the lower portion ofside member 60 and the frame 52 and oppositely arranged in like manner,each of which is operably connected to individual spray nozzle means 112and 112'. The nozzle means 112 and 112 are identical and both comprise atubular conduit or manifold 114 having a plurality of spray nozzles 116,see FIG.

19, spaced along the side of the conduit facing the cutting edge of theblades 78, 78 as they contact the pavement during cutting and grindingthereof, thereby spraying water for coating the blades or disks of thecutting units 48 and 50, respectively. As better seen in FIG. 14, anozzle spray means for each cutter or grinder init is attached at thefree closed ends by brackets 118 and at the opposite ends by anadjustable bracket assembly, generally indicated at 120. The bracketassembly 120 is more clearly illustrated in FIG. 19, in which there isshown a spacer bar 121, which is secured to the inner lower portion ofthis ds member 60. 9 he. 123919.521?! P911122:

Also secured by bolt 122 is an adjustable arm 124 having one endprovided with a slot 125 and the other end provided with a bearing 126.Said bearing 126 is adapted to receive a communicating neck member 127of the conduit 114, which when mounted in said bearing is operablycoupled to the hoses 110 and 111, not shown, whereby water from tank 44can be pumped to the cutting blades.

In order to supply a continuous, uninterrupted flow of water to theblades 78, 78', there is provided a vacuum system, generally indicatedat 130 in FIG. 1, 2 and Th ystm ussqt rqt rnths watcrt ma hths sludgematerial created by the cutting or grinding of the pavement, to the tank44. The vacuum system comprises a vacuum pump 132 mounted to the endtank trailer 28. This pump is operated by motor 134 by means of drivebelt 135, as seen in FIGS. 1, 2 and 6. A vacuum is pulled from withinthe tank 44 through an outlet passage 136 located in the front upperwall of the tank cell 162a. The vacuum flow is indicated by arrows 137from the tank 44 through passage 136 into pumps 132 where it is pumpedto atmosphere through a manifold 138. As the pressure within the tank 44is reduced by the vacuum system 130, a flow of water andsludgg iscreated between the cutting assembly 45 and tank 44. This flow isaccomplished by establishing a vacuum chamber 140 which is defined by aflexible and elastic shro'ud, indicated generally at 142, having asomewhat qsta u wal or ta n 144 scu a d depending from frame 52. Saidchamber also includes an upper shield partition 145, see FIG. 14, toseal or close the top of the vacuum chamber 140. The lower edges 1 149of the side walls 144 of the vacuum chamber 140 form a sealing contactwith the pavement around the cutting units and the spray nozzles.Included within the vacuum chamber 140 is a plurality of suction nozzles146 which are operably connected to a rectangular manifold 147 connectedto conduits like 150, 152 and 160 in FIG. 6 which lead to said tank 44for returning the water and sludge to said tank.

Referring to FIGS. 9, 14 and 20, the suction nozzles 146 are attachedand depend downwardly from a rectangular tubular manifold 147. Themanifold 147 is adapted to receive conduits 150 and 152, see FIG. 9,which lead to an overhead junction manifold 154, see FIGS. 2 and 6, saidmanifold l54 having a single input connection to the tank 44 throughpipe 156, which is received in the upper rear portion of said tank tocomplete the return flow of the coolant and sludge to said tank. Asshown in FIG. 14, a back-up group of suction nozzles 158 may be employedto recover leakage about the trailing shroud. This additional group ofnozzles is supported by a tubular frame 159 acting as a manifold,

also connected to the 115635111 154 by a conduit 160 for return flowthrough pipe 156.

The schematic view of FIG. 6 shows the vacuum system with the shroud 142in sealing contact with pavement 104, followed by nozzles 158. Thearrows 161 show the return flow of the coolant through the conduit 150,152 and 160, then into manifold 154, and again arrow 161a showing flowthrough pipe 156 into the rear section of the tank 44 in the area havinga low pressure which is created by the vacuum system 130.

In order to accommodate an uninterrupted flow of water from the endtrailer unit 28, its tank 44 has a plurality of sections, or cells, 1620to 162k capable of holding large quantities of coolant, such as water106. As indicated in FIGS. 1 and 3, the tank 44 is fixedly secured tothe trailer frame members 40, 40a of the first railer unit 26 by meansof the trailer hitch or swivel bed 29. Tank 44 and the trailer 28 aresupported at the rear thereof by tandem vehicle wheels 165. Aconventional protective body or shell 166 is provided to enclose thetank 44 as indicated in FIGS. 1 and 3. Manhole covers 168, located aboveeach cell 162a to 162e provide access to the-cells so that filters 170,which are removably mounted to each inner cell wall 172, can be replacedor cleaned, see FIG. 6. The filters are supported in frames 174, saidframes being positioned about the edges of openings 176 in the lowercentral parts of partition walls 172, see FIGS. 3 and 5. As can be seenin FIG. 6, the return flow of water and sludge enters the upper rearcell 162:: of the tank and, as the heavier sludge material settles tothe bottom of the first cell, the light and smaller material will siftthrough the first filter and then on through to the next cell andfilter.

.lr shs w s s vs fil s wa s 9 rmwh m ter a tcTtrap the fine particles asthey pass through each successive cell to the last cell, from which thewater is then pumped back to the spray nozzles. It can be seen that thesludge material will settle to the bottom of the tank 44. Therefore,there is provided therein a clean-out opening indicated at 178 in thebottom of each cell or section 162a to 162s. There is also provided inthe upper part of each wall 172 apertures 179, see FIGS. 3 and 4,whereby communication between each cell is accomplished so that apressure drop is readily facili- Referring back to the cutting units 48and 50, which in the previous description were described as beingadjustable with relation to transporting and the accommodation thereofto different angular configurations of the road beds, there will now bedescribed the cutting units with respect to the cutting and grindingmodes of operation.

FIG. 12 shows a cross-sectional view of the cutting unit 50 which hasthe blades 78' securely fixed on shaft 74, the similar cutting unit 48having blades 78 fixed on shaft 72. As shown in FIGS. l2, l3 and 22, forgroove cutting purposes the blades 78, 78' are evenly spaced apart asuitable distance, generally about three-fourths of an inch on center,as required to cut a kerf of about one-eighth of an inch deep, asindicated at B. For bump cutting purposes the blades like 78, 78' areclosely spaasdtasw llm snou For 522v; cutting purposes, each end of eachcutter 48 and 50 is provided with a depth control device. For thispurpose, as indicated in FIG. 11, cutter unit 48 has at its oppositeends the depth control devices 184 and 184a: and cutter unit 50 at itsopposite ends has the depth control devices 185, 185a. Each depthcontrol device is carried by a support bracket like 186 welded to theframe 52 for the outer ends of the cutters and welded to the floatingbeams 88 and for the inner ends of the cutters As shown in FIGS. 23 and26, bracket 186 is in the form of a box channel 251 acting as a shelfwelded at its end 252 to the member 253 which represent either thefloating beam or the frame member. The flat top shelf 251. The plates257 and 258 are rectangular and with the adjoining top 254 of the shelf25] form a space which receives the top of either the arm 188 of thedepth control device 185 in FIG. 12 or the top of the arm 250 of thedepth control device 284 in FIG. 23. The plates 257 and 258 have alignedholes 259 and 260 to receive the shaft 261 of a bolt 189 having a head262 behind plate 257 and at its front end having threads 263 for a nut264.

All four of these depth control devices for groove cutting are alike;and one of them, namely 185 at the outer end of cutter 50, is shown inelevation in FigIG. 12 wherein the frame member 60 has a bracket 186, tebolt 189 acting as a pivot support for the top of an inverted U-shapedrocker arm 188 having depending arms 188a and 188b. Arm 1880 is at thefront of the cutter 50 and terminates in a roller or wheel 190 whichrides on the pavement ahead of the cutter. Arm 118b extends behind thecutter and has a pivotal support at 194 for an adjusting arm 192 whichterminates at its lower end in a roller or wheel support 193 which rideson the pavement behind the cutter. The angular position of arm 192, andhence the depth that the cutter can cut into the pavement, is controlledby operating the adjusting screw 196 mounted in the arm 192 and bearingagainst an abutment 183 on arm 188b.

For bump cutting process, a modified form of depth control is providedfor each end of each cutter unit, a typical one being shown at 284 inFIGS. 23 and 26 wherein, after unfastening bolt 189 to remove each ofthe depth control devices like 184, each bracket like 186 is employed tosupport a depth control device like 284 which has a single arm 250 whichdoes not oscillate, but instead is rigidly fixed in the bracket. Forthis purpose, a wedge 264 is inserted between the top 254 of the shelf251 and the underside of arm 250, being removably held in position byscrews like 266 having threaded engagement with the top 254 of the shelf251. The wedge 265 as shown in FIG. 23 extends on opposite sides of avertical plane through the bolt 189 so that the arm 250 cannot swingeither up or down about the axis of the bolt. The top 267 of the wedge265 may be curved as shown in FIG. 23, or otherwise shaped to conform tothe shape of the undersurface of the arm 250. As shown in FIG. 26, thearm 250 is in the form of a hollow tube rectangular in cross section;and this form is preferred also for the depth control 188 in FIG. 12. Asthe arm 250 in FIGS. 23 and 26 is fixed in position, the nut 264 isscrewed down tight. In FIG. 23, the arm 292, adjusting screw 296, pivot294 and roller or wheel 293 are of the same construction and serve thesame purpose as described for the corresponding elements shown in FIG.12.

It is apparent, therefore, that the bracket 186 may be used for eitherl'orm ot'depth control shown in FIG. 12 or FIGS. 23 and 26. I

The depth control shown in FIG. 12 makes it possible to keep a veryclose tolerance on the depth of the kerf being cut, even when thesurface of the pavement 104 raises or lowers during a cutting pass, suchas shown in FIG. 18. Since the center of the cutting unit isintermediate that of the two rollers 190, 193, any raising or loweringof a roller with respect to the other roller will cause only a slightrise to the cutting area of the blade 78 That is, if the rollers 193 onthe rearward side of the blades are thus one inch above the levelpavement,

then e cutt r x s is ai e aly -ha f th amount because of the armsinvolved. It should be noted, at this time, that the above descriptionis with respect to the grooving operation of the machine.

When the machine is to be used as a leveling machine to level high spotsor areas on the road beds that have imperfections, as seen in FIG. 23,rollers 191] and the front portion 1880 of arm 188 are removed, therebyleaving only the trailing adjustable roller like 293 attached to oneportion of the arm like 250. Prior to the leveling operation, additionalblades are added to the cutter units 48 and 50 so that no space is leftbetween adjacent blades and a smooth surface can thereby be cut byadjusting the height of the cutter blades through the proper setting ofrollers like 293.

Referring to FIGS. 1 and 17, there is shown a temperature-responsivemeans, indicated generally at 197, located adjacent the trailing cuttingedges of the blades 78, said temperature-responsive means checkingwhether the cutters are being overworked due to the speed of travel. Atrough member 198 is extended downwardly from the frame 52, providing apickup for some of the sludge kicked off the cutter blades, said troughhaving a thermal couple 199 connected to a signal light (not shown)which is illuminated a s a warning signal if the sludge becomes too hot,thereby allowing corrective action so that the diamond blades 881111.ins b a .7

There is provided a separate means for laterally adjusting the positionof frame 52 by repositioning hitch 55 and the slot means 58, whichallows the shifting of the outer ends of the cutter units to bepositioned closely adjacent to a curb 105, as seen in FIG. 16. It ispossible to extend the outer cutter blades to within 12 inches of saidcurb. When the frame 52 is needed to be laterally moved, the hydrauliccylinders are also relocated on additional brackets secured to theunderside of the transverse beam 100, as shown in phantom lines in FIG.10. In FIG. 11 the phantom lines show the relocation f hitch 55, alongwith frame 52.

It is undesirable for the Diesel engine 16 in the tractor 12 to operatea low gear and directly drive the equipment at slow speed because itwould damage the blades 78, 78' if they met an obstruction. Hence, ahydraulic drive from the engine 16 is provided, as indicated in the flowdigram in FIG. 24 and in FIG. 25.

Engine 16 has a conventional clutch 200. Motor 234 is connected to theinput of a four-speed transmission ni T1 y a belt. and Pul yrangement 1. .9r t ,1v a 207. Transmission unit T2 has connect T2 ingear or in idle poition out of gear. T1 has a four-peed geartransmission controlld by handle H2. hen handle H1 is operated to makeT2 idle, engine 16 drives through the four-speed transmission t-to thedrive shaft 242 and differential D and the wheels 24. This conditionprevails when traveling at comparatively high speed from one location toanother one with the cutters in raised idle position. At this time fluidpressure retained in the cylindres hold the cutter in elevated position,a suitable catch, not shown, being provided, if desired.

When it is desired to cut bumps or grooves, the equipment is moved atcomparatively slow speed, the engine 16 at this time driving the pumpsP1, P2 through the five-speed transmission T5 and belt and pulleyarrangements 206 and 208, the clutch handle H3 being o perated todisconnect the engine lj from the wheels 24 which are then driven by thefluid motor 234 through the transmissions T1 and T2. The handles 201 and202 for the power take-off can be operated to either engage or disengagethe drive of pumps P1 and P2 with respect to the engine 16, as indicatedby arrows 203 and 204.

The fluid pressure from pump P1 is used to supply pressure to the twohydraulic cylinders 96 and 97, and the two small hydraulic cylinders 101and 102. The pressure fluid line 210 leads from the pump P1 to controlvalves 212 and 213, then through lines 214 and 215 to operate onecylinder 97, and through similar lines 216 and 217 to operate the secondcylinder 96, the lines 214 and 216 being provided with pressure gaugesG1 and G2 and pressure relief valves 218 and 220, respectively. Therelief valves 218 and 220 have lines like 221 connected to an oilreserve tank 222. A return line connects the oil reserve tank to thepump P1, and line 223 connects tank 222 to pump P2. The small cylinder101 is operably connected to pump Pl through fluid lines 210, 224 and225, said line 225 being provided with a pressure gauge G4 and apressure relief valve 2 26 between the cylinder and the I control valve228, said valve 228 receiving fluid pressure from line 210. The cylinder102 is connected to pump Pl through fluid lines 210, 209 and 211. Line209 is provided with a pressure gauge G3 and a relief valve 219 betweenthe cylinder and the control valve 205. Pump P2, supplies pressurethrough line 230 and filter F to line 230a leading to a power-steeringdevice 229 which operates the cylinder 231 operably attached to thefront steering wheels 22 of the tractor 12. Flow lines 232 and 233service the cylinder 231 between the steering device 229 and alsoprovide a reservoir return line 233a from the device 229 to thereservoir 222. Pressure line 230, in addition, via line 23% suppliespressure to operate fluid motor 234 through a control valve 236. Eachcontrol valve 212, 213, 205, 236 and 228 is connected to the reservetank 222 by return line 235. Lines 237 and 238 supply the pressure fluidfrom said valve 236 to the motor 2 34.

The pressure relief valves like 2 18 insure that a suitable value ofpressure is always available to operate the cylinders, the pump P1 beingoperated to supply a pressure in excess of the desired pressure, thesurplus being by-passed. The gauges G1 to G4 are arranged on a suitablepanel 246 adjacent the drivers seat 244 so that he can inspect thepressure being supplied to each cylinder and operate the valves like112, 213, etc., accordingly.

The modifications shown in FIGS. 27 to 29 have a number of features incommon with the form shown in FIG. 20. These common features includeupright frame members in the form of I-beams like 36' and 36 having acrosspiece like 37 carrying one member of a hitch like 55, the companionhitch member being on a header like 54 having a hinge connection like 53on a transverse horizontal axis with the forward ends of the U-shapedframe like 52, the header also having a hinge connection on the sameaxis with the floating beams for supporting the cutters, and hydrauliccylinders being provided for operating the frame and the floating beams.

In the form shown in FIG. 27, two cutters are employed, cutter 300having its outer end 201 carried by a bearing on floating beam 302having a hinge connection 318 with header 354 on the same horizontalaxis as the other hinges in FIG. 27. The inner end 303 of cutter 300 hasa bearing support in a frame member 304 which is fixed at its rear end305 to the U-shaped frame 352, while having a hinge connection 306 withheader 354 on the above-mentioned horizontal axis. Cutter 307 has aninner end 308 having a shaft which overlaps the shaft of the inner end303 of cutter 300. The inner end 308 has a bearing support in a framemember 309 having a rear end 310 fixed to the frame 352 and having afront end having a hinge connection 311 with header 354 on theabove-mentioned horizontal axis. The outer end 312 of cutter 307 has abearing support in a floating beam 313 having a forward end having ahinge connection 314 with header 354 on the horizontal axis. Like FIG.20, FIG. 27 shows upright frame members 336, 336 having a crosspiece 337which carries one member of a hitch 335, the companion member beingcarried by header 354. Frame 352 has a hinge connection 353 between eachof its side members and the header 354. All of the hinge connectionswith header 354 are on the same transverse horizontal axis.

FIG. 27 shows the inner ends of cutters 300 and 307 spaced apart thesame distance as the cutting disks as described in connection with FIG.20, for groove cutting purposes.

The construction of the rear ends of the floating beams in all the formsin FIGS. 27 to 29 is like the construction shown in FIG. 20. Inparticular, in FIG. 27, the cylinder 315 which operates the frame, hereshown as a single cylinder at the center of the frame, is operative toraise the frame and carry with it the rear ends of the floating beams tolift the cutters to idle position.

As in FIG. 20, in all the forms in FIGS. 27 to 29 the weight of theengine which drives the cutters is carried by the frame, being mountedon the side members like 60 and 60' in FIG. 20 whereby the weight of theengine is effective to hold down the outer ends of the cutters tocutting engagement with the pavement. The inner ends of the cutters inFIG. 20 are urged to cutting position by cylinders 101 and 102, whereasin FIG. 27 the outer end of cutter 300 is urged into cutting position bya cylinder 316 at the rear of the floating beam 302, the outer end ofcutter 307 being urged to cutting position by a cylinder 317 at the rearof beam 313.

For example, the cylinders 101 and 102 in FIG. 20 may have a throw ofone-and-one-half inches each side of a mean position, the pistons ofthese cylinders having a diameter of two-and-one-half inches. Cylinders96, 97 may have a throw of 16 inches, their pistons having a diameter of3 inches. When in cutting position, the weight of the engine holds theouter ends of the cutters in FIG. 20 to the work so that the totaldownward force on the outer ends of the cutters is equal to that weightplus the adjustable force provided by cylinders 96, 97. A somewhathigher pressure is supplied to the cylinders 101, 102 to equalize thepressure on the outer ends of the cutters because the downward pressureon the inner ends of the cutters is not influenced by the weight of theengine, but is due solely to the pressure exerted by the cylinders 101and 102.

In FIG. 28, a single cutter 319 is shown; and as indicated, this mayhave a length comparable to the overall length of the two cutters ofFIG. 27. One end 320 of cutter 319 has a bearing carried by floatingbeam 321 having a hinge connection 322 with the header 323, the rear endof beam 321 having a hydraulic cylinder 324 to urge the associated endof the cutter to cutting position. the other end 325 of cutter 319 has abearing support in floating beam 326 having a pivotal connection 327with the header, the rear end of beam 326 having a cylinder 328 forurging the cutter to cutting position. At the center of the U-frame 329is provided a hydraulic cylinder 330 for lifting cutter 319 to idleposition.

In FIG. 29, the U-frame 331 is operated by a hydraulic cylinder 332 atthe rear center of the frame. Two cutters are shown, cutter 333overlapping the inner end of cutter 334 as indicated at 335, for bumpcutting purposes. The opposite ends of cutter 333 are mounted infloating beams 356 and 357. Te opposite ends of cutter 334 are mountedin floating beams 358 and 359. Each of the floating beams and each ofthe side members of frame 331 has a hinge connection on axis AA with theheader 360. Each floating beam has a hydraulic cylinder as indicated at361, 362, 363 and 364. The cylinders in FIG. 29 serve the same purposeas described in connection with FIGS. 20, 27 and 28.

In FIGS. 27 to 29, a universal bearing is provided for each end of eachcutter, similar to the showing in FIG. 21 previously described.

The invention and its attendant advantages will be understood from theforegoing description and it will be appalept that various changes maybe made in the form, construction and arrangement of the parts of theinvention without departing from the spirit and scope thereof orsacrificing its material advantages, the arrangements hereinbeforedescribed being merely by way of example; and I do not wish to berestricted to the specific forms shown or uses mentioned, except asdefined in the accompanying claims.

We claim:

1. High or low power drive for pavement groover or grinder wherein anengine is provided with clutch and a first transmission unit for drivingthe traction wheels of a vehicle, said vehicle including a pavementleveling or grooving machine, the improvement wherein an alternativehydraulic drive is operated by said engine when said engine isdisconnected from said traction wheels, said hydraulic drive comprisinga hydraulic pump driven by said engine, a hydraulic motor operated bysaid pump and having a driving connection through said firsttransmission unit with said traction wheels.

2. Drive according to claim 1, said pavement leveling or groovingmachine including a rotary cutter, including another hydraulic pumpoperated by said engine wlEn the same is disconnected from said tractionwheels, hydraulic cylinder means in circuit with said other pump forraising or lowering said rotary cutter,

a pressure relief valve for limiting the fluid pressure supplied fromsaid first-mentioned pump to said motor, and another pressure reliefvalve for limiting the pressure supplied to said hydraulic cylindermeans.

3. Drive according to claim 1, and including a second transmission unithaving a clutch handle to connect said first transmission unit in gearor in idle position out of gear, and a driving connection from saidhydraulic motor to said second transmission unit.

4. Drive according to claim 1, wherein said pump is driven by saidengine through a multi-speed transmission and belt and pulleyarrangement, a clutch handle being provided to disconnect said enginefrom said traction wheels when said wheels are driven by said hydraulicmotor.

5. High power, high speed or low power, low speed drive for a vehiclehaving an engine with a clutch anfirst transmission unit for driving thetraction wheels of said vehicle, the improvement wherein an alternativehydraulic drive is operate by said engine when said engine isdisconnected from said traction wheels, said hydraulic drive comprisinga power take-off from said engine to a fluid pressure pump formaintaining an excess fluid pressure, a hydraulic motor operated by saidpump and having a driving connection through said first transmissionunit at low speed to said traction wheels, and a pressure relief valvefor by-passing pressure in excess of a desired value to maintain adesired minimum pressure for operating said motor.

6. Pavement cutting machine comprising a vehicle having an engine andfirst transmission unit for driving traction wheels, an alternativehydraulic drive comprising a hydraulic pump operated by said engine anda hydraulic motor driven by said pump for driving said traction wheelsat certain times, said vehicle having a cutter, meas for raising orlowering said cutter, said engine being operative to drive said tractionwheels through said first transmission unit at comparatively high speedwith said cutter in idle raised position at certain times, said enginebeing operative to drive said traction wheels through said firsttransmission unit by said hydraulic drive at comparatively slow speed atother times with said cutter in operative relation with said pavement,and a separate engine for operating said cutter.

7. High or low power drive for pavement cutting machine wherein anengine is provided with clutch and a main transmission for driving atraction wheels of a vehicle at high speed, said vehicle having atrailer having a pavement cutting machine driven by another engine, analternative hydraulic drive operated by said engine when said engine isdisconnected from said traction wheels, said hydraulic drive comprisinga fluid pressure pump driven by said engine, and a hydraulic motoroperated by said pump and having a driving connection through saidtransmission with said traction wheels.

8. High or low power drive for pavement groover or grider wherein anengine is provided with a clutch and a first transmission unit fordriving the traction wheels of a vehicle, said vehicle including apavement leveling or grooving machine, the improvement wherein an aln te hyq as iq ve is mate b s id en when said engine is disconnected fromsaid traction wheels, said hydraulic drive comprising a first hydraulicpump driven by said engine, a hydraulic motor operated by said firsthydraulic pump and having a driving connection through said firsttransmission unit with said traction wheels, a rotary cutter, a separateengine for operating said cutter, a second hydraulic pump operated bysaid engine when the same is disconnected from said traction wheels,hydraulic cylinder means in circuit with said second pump for raising orlowering said t ry utt r.anrqssunl va vc qr im in the fluid pressuresupplied from said first-mentioned pump to said motor, and anotherpressure relief valve for limiting the pressure supplied to saidhydraulic cylinder means, and a power takeoff and driving connection atopposite sides of said first-mentioned engine for operating said firstand second pumps respectively.

1. High or low power drive for pavement groover or grinder wherein anengine is provided with clutch and a first transmission unit for drivingthe traction wheels of a vehicle, said vehicle including a pavementleveling or grooving machine, the improvement wherein an alternativehydraulic drive is operated by said engine when said engine isdisconnected from said traction wheels, said hydraulic drive comprisinga hydraulic pump driven by said engine, a hydraulic motor operated bysaid pump and having a driving connection through said firsttransmission unit with said traction wheels.
 2. Drive according to claim1, said pavement leveling or grooving machine including a rotary cutter,including another hydraulic pump operated by said enging when the sameis disconnected from said traction wheels, hydraulic cylinder means incircuit with said other pump for raising or lowering said rotary cutter,a pressure relief valve for limiting the fluid pressure supplied fromsaid first-mentioned pump to said motor, and another pressure reliefvalve for limiting the pressure supplied to said hydraulic cylindermeans.
 3. Drive according to claim 1, and including a secondtransmission unit having a clutch handle to connect said firsttransmission unit in gear or in idle position out of gear, and a drivingconnection from said hydraulic motor to said second transmission unit.4. Drive according to claim 1, wherein said pump is driven by saidengine through a multi-speed transmission and belt and pulleyarrangement, a clutch handle being provided to disconnect said enginefrom said traction wheels when said wheels are driven by said hydraulicmotor.
 5. High power, high speed or low power, low speed drive for avehicle having an engine with a clutch and first transmission unit fordriving the traction wheels of said vehicle, the improvement wherein analternative hydraulic drive is operated by said engine when said engineis disconnected from said traction wheels, said hydraulic drivecomprising a power take-off from said engine to a fluid pressure pumpfor maintaining an excess fluid pressure, a hydraulic motor operated bysaid pump and having a driving connection through said firsttransmission unit at low speed to said traction wheels, and a pressurerelief valve for by-passing pressure in excess of a desired value tomaintain a desired minimum pressure for operating said motor. 6.Pavement cutting machine comprising a vehicle having an engine and firsttransmission unit for driving traction wheels, an alternative hydraulicdrive comprising a hydraulic pump operated by said engine and ahydraulic motor driven by said pump for driving said traction wheels atcertain times, said vehicle having a cutter, means for raising orlowering said cutter, said engine being operative to drive said tractionwheels through said first transmission unit at comparatively high speedwith said cutter in idle raised position at certain times, said enginebeing operative to drive said traction wheels through said firsttransmission unit by said hydraulic drive at comparatively slow speed atother times with said cutter in operative relatIon with said pavement,and a separate engine for operating said cutter.
 7. High or low powerdrive for pavement cutting machine wherein an engine is provided withclutch and a main transmission for driving the traction wheels of avehicle at high speed, said vehicle having a trailer having a pavementcutting machine driven by another engine, an alternative hydraulic driveoperated by said engine when said engine is disconnected from saidtraction wheels, said hydraulic drive comprising a fluid pressure pumpdriven by said engine, and a hydraulic motor operated by said pump andhaving a driving connection through said transmission with said tractionwheels.
 8. High or low power drive for pavement groover or grinderwherein an engine is provided with a clutch and a first transmissionunit for driving the traction wheels of a vehicle, said vehicleincluding a pavement leveling or grooving machine, the improvementwherein an alternative hydraulic drive is operated by said engine whensaid engine is disconnected from said traction wheels, said hydraulicdrive comprising a first hydraulic pump driven by said engine, ahydraulic motor operated by said first hydraulic pump and having adriving connection through said first transmission unit with saidtraction wheels, a rotary cutter, a separate engine for operating saidcutter, a second hydraulic pump operated by said engine when the same isdisconnected from said traction wheels, hydraulic cylinder means incircuit with said second pump for raising or lowering said rotarycutter, a pressure relief valuve for limiting the fluid pressuresupplied from said first-mentioned pump to said motor, and anotherpressure relief valve for limiting the pressure supplied to saidhydraulic cylinder means, and a power takeoff and driving connection atopposite sides of said first-mentioned engine for operating said firstand second pumps respectively.